CN212155145U

CN212155145U - Scroll compressor having a discharge port

Info

Publication number: CN212155145U
Application number: CN202020738767.5U
Authority: CN
Inventors: 赵灿杰; 金洙喆; 权益贤
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2019-06-19
Filing date: 2020-05-07
Publication date: 2020-12-15
Anticipated expiration: 2030-05-07
Also published as: US20200400144A1; KR20200144813A; US11415132B2

Abstract

A utility model relating to a scroll compressor is provided. The proposed utility model is characterized in that, a guide groove is formed in any one of the fixed scroll and the swirl scroll, and an anti-rotation member is provided on the other side, which can be inserted into the guide groove and revolved inside it to prevent the swirl scroll from rotating.

Description

Scroll compressor having a discharge port

Technical Field

The present invention relates to a compressor, and more particularly, to a scroll compressor.

Background

The compressor is a device that compresses fluid such as refrigerant gas, etc., and may be classified into a rotary compressor, a reciprocating compressor, a scroll compressor, etc., according to the way the fluid is compressed.

A scroll compressor is a compressor including two scrolls. According to this scroll compressor, when the two scrolls perform a relative orbiting motion, a plurality of compression chambers are formed between the two scrolls, and the volume of the compression chambers decreases as the compression chambers continue to move in the center direction, whereby the refrigerant is continuously sucked, compressed, and discharged.

The scroll compressor has an advantage of being able to obtain a relatively high compression ratio as compared with other types of compressors, and has an advantage of being able to obtain a stable torque since suction, compression, and discharge strokes of a refrigerant can be smoothly engaged, and thus is widely used for compression of a refrigerant in air conditioning equipment and the like.

Such a scroll compressor can be classified into a low pressure type scroll compressor and a high pressure type scroll compressor according to whether suction gas or discharge gas is filled in the interior of a casing thereof. Among them, the low pressure type scroll compressor may be configured to include a motor and a compression part.

The motor may include a driving motor composed of a rotor and a stator, and a driving shaft rotated together with the rotation of the driving motor and formed with an eccentric portion at an upper portion thereof. A main frame is disposed between the motor and the compression part, and a suction pipe for allowing fluid to flow in from the outside may be provided in the motor.

The compression portion may be constituted by a swirl coil and a fixed scroll. The fixed scroll is fixed on the upper part of the main frame, and the orbiting scroll is arranged between the main frame and the fixed scroll. The orbiting scroll may be connected to the driving shaft and may orbit with the rotation of the driving shaft, and may compress the refrigerant sucked into the compression part when the orbiting scroll orbits by engaging with the fixed scroll.

The scroll compressor may include a Oldham Ring (Oldham Ring) as a rotation prevention mechanism for rotating the orbiting scroll within the fixed scroll, and a discharge pipe for discharging the refrigerant compressed in the compression portion to the outside.

The cross ring is disposed between the main frame and the orbiting scroll, and may be configured to include an annular body and a key protruding from the body toward the orbiting scroll. The orbiting scroll may include a disk-shaped end plate and an orbiting wrap formed to protrude in a thickness direction of the end plate. In addition, a key groove is arranged on the bottom surface of the end plate, which is opposite to the cross ring and the main frame. That is, the key groove is provided on the surface of the end plate opposite to the surface on which the swirl lap is arranged.

The key groove is formed to be recessed at the bottom surface of the end plate, and the coupling between the swirling disc and the spider can be achieved by inserting a key into such a form of the key groove. The key groove has a length extending in a diameter direction of the end plate so that the key of the cross ring can move inside the key groove. In addition, the key groove penetrates the end plate and opens to the outside in the diameter direction of the end plate, and the key of the cross ring can enter and exit the key groove through the open passage.

One of the important problems in such a scroll compressor is a problem of leakage and lubrication between the fixed scroll and the orbiting scroll. That is, in order to prevent leakage between the fixed scroll and the orbiting scroll, the end of the wrap should be in close contact with the surface of the end plate so that the compressed refrigerant does not leak. In other words, the end plate of the fixed scroll may be in close contact with the lap of the orbiting scroll, and the end plate of the orbiting scroll may be in close contact with the lap of the fixed scroll.

On the other hand, in order to allow the orbiting scroll to smoothly orbit relative to the fixed scroll, the resistance caused by friction should be minimized, but the leakage and lubrication problems are in an opposite relationship to each other. That is, if the end of the scroll portion and the surface of the end plate portion are strongly brought into close contact, although it is advantageous in terms of leakage, noise and damage due to abrasion are increased due to increased friction. Conversely, if the grip strength is lowered, the friction is reduced, but the sealing force is lowered, thereby increasing leakage.

Thus, the prior art has addressed the problem of sealing and reducing friction by forming a back pressure chamber on the back of the orbiting or fixed scroll that has an intermediate pressure defined by the intermediate value of the discharge and suction pressures.

The back pressure chamber communicates with a compression chamber having an intermediate pressure among a plurality of compression chambers formed between the orbiting scroll and the fixed scroll. The pressure acting in such a back pressure chamber functions to bring the orbiting scroll into proper close contact with the fixed scroll, whereby the problems of leakage and lubrication can be solved to some extent.

On the other hand, the back pressure chamber may be located on a bottom surface of the orbiting scroll or an upper surface of the fixed scroll, and for convenience, may be referred to as a lower back pressure scroll compressor and an upper back pressure scroll compressor, respectively.

In the case of the lower back pressure scroll compressor, there are advantages in that the structure is simple and it is easy to form a bypass hole, etc. In the lower back pressure scroll compressor, a back pressure chamber is formed in a bottom surface of the orbiting scroll, more specifically, a bottom surface of the end plate.

However, not only the back pressure chamber but also the key groove is formed in the bottom surface of the end plate of the orbiting scroll. At this time, the back pressure chamber is formed along the circumferential direction of the end plate, and the key groove is formed along the diameter direction of the end plate.

If the back pressure chamber and the key groove are arranged to overlap, the back pressure chamber cannot be normally formed. Further, due to the characteristics of the back pressure chamber communicating with the compression chamber having an intermediate pressure among the plurality of compression chambers, the position of the back pressure chamber is difficult to be deviated from a specific position, for example, an intermediate point between the center in the diameter direction of the end plate and the outer peripheral surface of the end plate.

Therefore, the key groove can be disposed only between the outer peripheral surface of the end plate and the outer peripheral surface of the end plate. However, when the key groove is arranged in the above-described manner, only the size of the end plate of the orbiting scroll can be increased accordingly due to the characteristic of the key groove that should extend in the diameter direction of the end plate, thereby causing a problem that the size of the scroll compressor is unnecessarily increased.

SUMMERY OF THE UTILITY MODEL

Problem to be solved by the utility model

An object of the utility model is to provide a scroll compressor, it has compact size, can also provide the performance that obtains further improvement.

Further, another object of the present invention is to provide a scroll compressor having an improved structure, which can improve compression alignment accuracy.

Further, another object of the present invention is to provide a scroll compressor having an improved structure, which can reduce manufacturing difficulty and manufacturing cost.

Means for solving the problems

In order to achieve the above object, according to one aspect of the present invention, there is provided a scroll compressor in which a guide groove is formed in either one of a fixed scroll and a orbiting scroll, and a rotation preventing member is provided on the other side, the rotation preventing member being inserted into the guide groove and revolved inside the guide groove to prevent rotation of the orbiting scroll.

Here, the guide groove may be formed on one side surface of the swirl end plate from which the swirl coil protrudes.

In addition, another aspect of the present invention is characterized in that a back pressure chamber formed to form an intermediate pressure is disposed in the main frame.

According to this configuration, the configuration relating to the formation of back pressure and the configuration relating to the prevention of the rotation of the orbiting scroll can be respectively arranged at positions that do not affect each other at all, so that the scroll compressor having a compact size and excellent performance can be provided.

According to an aspect of the present invention, a scroll compressor includes: a case having a closed inner space; a fixed scroll disposed in an inner space of the casing; a swirling disc combined with the fixed scroll to form a compression chamber and performing a swirling motion; and a main frame supporting the orbiting scroll and having a back pressure chamber formed at a side opposite to the orbiting scroll to communicate with the compression chamber, the orbiting scroll including: a swirl coil engaged with the fixed scroll to form the compression chamber; a swirl end plate disposed between the swirl coil and the main frame; and a back pressure hole formed to penetrate the orbiting end plate to communicate the compression chamber and the back pressure chamber with each other, wherein a guide groove is formed in one of the fixed scroll and the orbiting scroll, and a rotation preventing member is provided in the other of the fixed scroll and the orbiting scroll, the rotation preventing member being inserted into the guide groove so as to be capable of revolving inside the guide groove.

Further, it is preferable that the guide groove is formed in a side surface of the swirl end plate from which the swirl coil protrudes.

Further, preferably, the guide groove is formed to be recessed in a side surface of the whirl end plate opposite to the fixed scroll, and the rotation preventing member is provided to the fixed scroll and is provided to be protruded toward the guide groove.

Further, it is preferable that, in the fixed scroll, a concave installation groove is formed, and the rotation prevention member is tightly fitted to the installation groove so that at least a part of the rotation prevention member protrudes toward the guide groove.

Further, preferably, the fixed scroll includes: a stationary end plate disposed opposite the swivel end plate; and a fixed scroll portion disposed between the orbiting end plate and the fixed end plate to mesh with the orbiting scroll portion to form the compression chamber, the fixed scroll portion and the installation groove being formed in the fixed end plate and on a surface opposite to the orbiting end plate.

Further, it is preferable that the rotation preventing member is formed to have a length longer than a depth of the installation groove and shorter than a distance between the guide groove and a bottom surface of the installation groove facing each other.

Further, it is preferable that the rotation prevention member is provided in a pin shape formed with a predetermined diameter, and the guide groove is formed in a circular groove having a diameter larger than that of the rotation prevention member.

Further, preferably, the present invention further comprises a ring inserted into the guide groove, wherein the rotation preventing member is in contact with an inner circumferential surface of the ring and revolves around an inner region of the ring.

Further, preferably, the main frame includes: a first support portion configured to be opposed to the other side surface of the whirl end plate to support the whirl coil; and a second support portion disposed at an outer side in a diameter direction of the first support portion to be coupled with the fixed scroll, the back pressure chamber being formed to be recessed in the first support portion.

Further, preferably, the back pressure chamber is formed to be recessed from a side surface of the first support portion opposite to the whirl end plate toward a direction away from the whirl end plate, and is formed in a ring shape surrounding a center in a diameter direction of the first support portion.

Further, preferably, a pair of the back pressure chambers are arranged in the shape of concentric circles.

Further, it is preferable that the guide groove is provided as a circular groove formed such that the length of the diameter thereof corresponds to or is less than or equal to the interval between the pair of back pressure chambers.

Furthermore, the present invention preferably further comprises a sealing member disposed between the swirling coil and the main frame and disposed in the back pressure chamber.

Further, preferably, the sealing member includes: a close-fitting section disposed between the rotating end plate and the back pressure chamber so as to be able to closely fit to the rotating end plate; and a support part, at least a part of which is inserted into the back pressure cavity and connected with the clinging part.

Further, it is preferable that the support portion is formed as a surface extending in a direction connecting the whirl end plate and the back pressure chamber to each other, the close contact portion is formed as a surface parallel to the whirl end plate, and the support portion is connected to the support portion between the whirl end plate and the close contact portion.

Effect of the utility model

According to the scroll compressor of the present invention, it is possible to provide a scroll compressor having a compact size and excellent performance without unnecessarily increasing the size of the swirling disc due to the constitution related to the formation of back pressure and the constitution related to the rotation of the non-swirling disc.

Furthermore, according to the utility model discloses, can form back vortex book portion and guiding groove simultaneously at a face of vortex dish that circles round, make fixed vortex book portion and setting up the groove and form the position that can see simultaneously in a direction to can carry out the processing of returning vortex book portion and the processing of guiding groove simultaneously, can carry out the processing of fixed vortex book portion and the processing that sets up the groove simultaneously moreover.

Therefore, the utility model discloses can come to the guiding groove with the position and the shape of setting for and carry out accurate processing with setting for the groove to can provide the effect that improves compression alignment accuracy.

Furthermore, the utility model discloses can go on simultaneously returning the processing of vortex winding and the processing of guiding groove, can carry out the processing of fixed vortex winding and the processing that sets up the groove simultaneously moreover to not only can reduce the processing degree of difficulty of fixed vortex dish and the vortex dish of circling round, but also have the effect that can reduce required work load and manufacturing cost when making fixed vortex dish and returning the vortex dish.

Furthermore, the present invention adopts a structure in which the back pressure chamber is formed on the main frame instead of the orbiting scroll, and thus the possibility of the orbiting scroll tilting and the vibration and noise due to the tilting can be reduced as compared with the case in which the back pressure chamber is formed on the orbiting scroll.

Furthermore, the present invention adopts a structure in which the sealing member is provided in a form that is not fixed to any of the swirling coil and the main frame, and performs a sealing function by using the back pressure formed in the back pressure chamber, whereby the degree of wear of the sealing member can be remarkably reduced.

Drawings

Fig. 1 is a sectional view illustrating a structure of a scroll compressor according to an embodiment of the present invention.

Fig. 2 is an exploded plan perspective view illustrating the scroll compressor shown in fig. 1 in an exploded manner.

Fig. 3 is a bottom exploded perspective view showing the scroll compressor shown in fig. 2 in an exploded manner.

Fig. 4 is a bottom perspective view showing the fixed scroll shown in fig. 1 separated.

Fig. 5 is a plan perspective view showing the orbiting scroll shown in fig. 1 in a separated state.

Fig. 6 is a bottom perspective view of the orbiting scroll shown in fig. 1, shown separated.

Fig. 7 is a perspective view showing the main frame shown in fig. 1 separated.

Fig. 8 is a view illustrating a coupling structure between the rotation preventing member and the guide groove shown in fig. 1.

Fig. 9 is a sectional view illustrating a compression part structure of the scroll compressor shown in fig. 1.

Fig. 10 is an enlarged view showing a portion "x" of fig. 9 in an enlarged manner.

Fig. 11 is a sectional view showing a sealing action of the sealing member shown in fig. 10.

Fig. 12 is a perspective view showing a cross ring of a compressor of the related art.

Fig. 13 is a bottom view showing a bottom surface of a swirling disc of a compressor in the related art.

Wherein the reference numerals are as follows:

100: scroll compressor having a discharge port

101: main bearing

103: secondary bearing

100: casing (CN)

111: suction inlet

113: discharge port

120: electric machine

121: stator

123: rotor

130: drive shaft

140: main frame

141: first drive shaft support part

142: second drive shaft support part

143: a first supporting part

145: second supporting part

147: back pressure cavity

150: fixed scroll

151: fixed end plate

152: discharge port

153: fixed scroll part

155: side wall part

157: frame joint

159: setting groove

160: spiral vortex disc

161: rotary end plate

162: back pressure hole

163: swirl coil

164: shaft coupling part

165: guiding groove

170: anti-rotation component

180: ring (C)

190: sealing member

191: clinging part

193: supporting part

Detailed Description

Hereinafter, an embodiment of a scroll compressor according to the present invention will be described with reference to the accompanying drawings. The thickness of lines or the size of components and the like shown in the drawings may be exaggerated for clarity and convenience of description for the sake of convenience of explanation. In addition, the latter term is a term defined in consideration of functions in the present invention, and may vary according to the intention or practice of a user or an operator. Therefore, the definitions of these terms should be determined based on the contents throughout the specification.

[ integral Structure of scroll compressor ]

Fig. 1 is a sectional view showing a structure of a scroll compressor according to an embodiment of the present invention, fig. 2 is a plan exploded perspective view showing a structure of the scroll compressor shown in fig. 1 in an exploded manner, and fig. 3 is a bottom exploded perspective view showing a structure of the scroll compressor shown in fig. 2 in an exploded manner.

Referring to fig. 1 to 3, a scroll compressor 100 according to an embodiment of the present invention includes: a casing 110, a motor 120, a driving shaft 130, a main frame 140, a fixed scroll 150, and a swirling scroll 160.

The casing 110 forms an external appearance of the scroll compressor 100 according to the present embodiment. An inner space for accommodating various components constituting the scroll compressor 100 is formed inside such a casing 110.

In the present embodiment, the case 110 is formed in a substantially cylindrical shape. The housing 110 may be provided with an inlet 111 and an outlet 113. The suction port 111 is a passage formed in the casing 110 to allow the refrigerant to flow into the casing 110, and the discharge port 113 is a passage formed in the casing 110 to discharge the refrigerant compressed in the casing 110 to the outside of the casing 110.

The inner space of the casing 110 may be divided into a motor part, which is a space in which the motor 120 is disposed, and a compression part, which is a space in which a refrigerant is compressed.

The motor 120 is accommodated in an inner space of the housing 110, more specifically, in a motor part. Such a motor 120 may be constructed including a stator 121 and a rotor 123. The motor 120 may be a constant speed motor in which the rotational speed of the rotor 123 is constant, or may be an inverter motor in which the rotational speed of the rotor 123 is variable.

A driving shaft 130 is connected to the rotor 123 of the motor 120, and the driving shaft 130 is rotated according to a rotational force generated by the motor 120. Such a driving shaft 130 may penetrate the main frame 140 to be coupled with the orbiting scroll 160, and the orbiting scroll 160 may be coupled with the driving shaft 130 to perform an orbiting motion.

The main frame 140 is disposed in an inner space of the casing 110, and may be disposed between the motor 120 and the orbiting scroll 160. The inner space of the casing 110 may be divided into a motor part and a compression part by the main frame 140.

A driving

shaft supporting portion

141, 142 is formed at the center of the main frame 140 in the diameter direction to support the driving shaft 130 penetrating the main frame 140. The drive

shaft supporting portions

141 and 142 may be provided with a main bearing 101, and the main bearing 101 may support the drive shaft 130 in a diameter direction of the main frame 140.

The fixed scroll 150 is accommodated in the inner space of the casing 110, more specifically, in the compression portion. The fixed scroll 150 is disposed closer to the discharge port 113 than the motor 120 disposed in the motor unit. The orbiting scroll 160 is disposed between the motor 120 and the fixed scroll 150. The orbiting scroll 160 is engaged with the fixed scroll 150 to form a compression chamber.

Further, an anti-rotation member 170 may be provided between the fixed scroll 150 and the orbiting scroll 160. The rotation preventing member 170 serves to prevent rotation of the check scroll 160 so that the orbiting scroll 160 can orbit in the fixed scroll 150.

In the scroll compressor 100 configured as described above, the refrigerant flows into the scroll compressor 100 through the suction port 111. The refrigerant flowing in this way flows into the compression section through the motor section. The refrigerant flowing into the compression portion flows into a compression chamber formed by meshing the orbiting scroll 160 and the fixed scroll 150, is compressed, and is discharged to the outside of the scroll compressor 100 through the discharge port 113 as a high-pressure refrigerant compressed in the compression chamber.

Unexplained reference numeral 107 denotes a cover which covers an upper portion of the fixed scroll 150 to support the fixed scroll 150 at an upper portion.

[ Structure of fixed scroll ]

Referring to fig. 1 to 4, the fixed scroll 150 may include a fixed end plate 151 and a fixed wrap 153.

The fixed end plate 151 is formed in a substantially circular disk shape and forms a flat surface. The fixed wrap 153 is formed to protrude from the fixed end plate 151 in the thickness direction of the fixed end plate 151. Such a fixed wrap 153 is formed to protrude from a surface of the fixed end plate 151 on a side opposite to the motor 120 toward the motor 120 side, and is engaged with the orbiting scroll 160 to form a compression chamber.

The discharge port may be formed at the fixed scroll 150. The discharge port forms a passage for discharging the refrigerant flowing into the compression chamber to the outside of the compression chamber. Such a discharge port may be formed to penetrate the fixed end plate 151 and disposed at a side closer to a central portion of the compression chamber than the suction port.

The discharge port is connected to a discharge port 113 provided in the casing 110. As a result, the high-pressure refrigerant compressed in the compression chamber and discharged to the outside of the compression chamber through the discharge port can be discharged to the outside of the scroll compressor 100 through the discharge port 113. The discharge port can be opened and closed by a valve 105 provided in the fixed scroll 150.

Further, the fixed scroll 150 may be provided with a side wall portion 155. The side wall portion 155 is formed to protrude from the fixed end plate 151 in the thickness direction of the fixed end plate 151, and may protrude in the same direction as the protruding direction of the fixed wrap portion 153. Such a side wall portion 155 may be formed in a manner to surround the fixed wrap 153 on the outer side in the diameter direction of the fixed scroll 150.

The side wall portion 155 is formed to have a relatively thicker thickness than the fixed scroll portion 153, so that it can contribute to the enhancement of the structural strength of the fixed scroll 150. The side wall 155 may provide a coupling surface required for coupling the rotation preventing member 170 to the fixed scroll 150, which will be described later. At this time, the side wall portion 155 is preferably formed to have a sufficient thickness required for coupling with the rotation preventing member 170 in consideration of the thickness of the rotation preventing member 170.

Further, the fixed scroll 150 may be provided with a setting groove 159. The arrangement groove 159 may be formed to be recessed in one side surface of the fixed scroll 150, more specifically, the side wall portion 155 opposite to the orbiting scroll 160. The installation groove 159 is provided for coupling the rotation preventing member 170 and the fixed scroll 150, which will be described later. The rotation preventing member 170 may be closely fitted to the installation groove 159, and the rotation preventing member 170 may be installed on the fixed scroll 150 by the close fit between the installation groove 159 and the rotation preventing member 170.

The setting groove 159 may be formed to be exposed in the same direction as the fixed scroll 150 in which the fixed wrap 153 is exposed. That is, the setting groove 159 may be formed at a position where the fixed scroll 153 and the setting groove 159 are simultaneously visible.

As described above, in the structure formed on the fixed scroll 150 at the position where the fixed scroll 153 and the disposition groove 159 are simultaneously visible, the fixed scroll 153 and the disposition groove 159 may be simultaneously processed. As described above, if the fixed scroll 153 and the installation groove 159 can be simultaneously processed, the installation groove 159 can be precisely processed in accordance with the position and shape of the installation groove 159 which are set in consideration of the position and shape of the fixed scroll 153.

Further, since the fixed scroll 153 and the installation groove 159 can be simultaneously processed in one processing operation, the number of steps and the manufacturing cost required for manufacturing can be reduced.

In addition, a frame coupling portion 157 may be further provided to the fixed scroll 150. The frame coupling portion 157 may be formed to protrude from the side wall portion 155 to the outside in the diameter direction of the fixed scroll 150. Such a frame coupling portion 157 is provided for coupling between the fixed scroll 150 and the main frame 140, and therefore can be coupled to a second support portion 145 of the main frame 140, which will be described later.

The fixed scroll 150 may be provided with a plurality of frame coupling portions 157, and the plurality of frame coupling portions 157 may be disposed at predetermined intervals along a circumferential direction of the fixed end plate 151.

[ Structure of swirling vortex disk ]

Fig. 5 is a plan perspective view showing the orbiting scroll shown in fig. 1 in a separated state, and fig. 6 is a bottom perspective view showing the orbiting scroll shown in fig. 1 in a separated state.

Referring to fig. 1, 5, and 6, the orbiting scroll 160 may include an orbiting end plate 161 and an orbiting scroll part 163.

The whirl end plate 161 may be formed in a substantially disk shape. On one side of such a swirl end plate 161, a plane may be formed opposite to the fixed end plate 151 of the fixed scroll 150. Further, a plane facing the main frame 140 may be formed on the other side of the whirl end plate 161.

The swirl coil 163 is formed to protrude from the swirl end plate 161 in the thickness direction of the swirl end plate 161. Such a swirl wrap 163 is formed to protrude from a side of the swirl end plate 161 toward a side of the fixed scroll 150 facing the swirl end plate 161, and is engaged with the fixed scroll 150 to form a compression chamber.

A shaft coupling portion 164 may be provided at the swirling coil 160. The shaft coupling part 164 may be provided at the whirl end plate 161, more specifically, at the other side surface of the whirl end plate 161 opposite to the rotation prevention member 170. The drive shaft 130 is coupled to the shaft coupling portion 164, and the coupling between the swirling scroll 160 and the drive shaft 130 can be achieved by the coupling between the shaft coupling portion 164 and the drive shaft 130. The shaft coupling portion 164 may be provided with a sub bearing 103 supporting the driving shaft 130 in a diameter direction of the orbiting scroll 160.

The shaft coupling portion 164 may be disposed at the center of the swirl end plate 161 in the radial direction, and the shaft coupling portion 164 may be eccentrically coupled to the drive shaft 130, whereby the swirl disc 160 may be eccentrically coupled to the drive shaft 130. As described above, the swirling coil 160 eccentrically coupled to the driving shaft 130 may swirl by the rotation of the driving shaft 130.

As described above, the rotation of the orbiting scroll 160 provided to be able to orbit may be prevented by the rotation preventing member 170 coupled to the orbiting scroll 160. A guide groove 165 is provided in the orbiting scroll 160 to combine the orbiting scroll 160 and the rotation preventing member 170. The guide groove 165 may be formed to be recessed in a side surface of the swirl end plate 161 opposite to the fixed end plate 151 of the fixed scroll 150.

The guide groove 165 is formed in the swirl end plate 161, and may be formed in a side surface of the swirl end plate 161 where the swirl wrap 163 is formed to be protruded. That is, the guide groove 165 is formed in the whirl end plate 161, and may be formed on the same surface of the whirl end plate 161 on which the whirl scroll portion 163 is formed.

As described above, in the structure in which the orbiting wrap 163 and the guide groove 165 are simultaneously formed on one surface of the orbiting end plate 161, the orbiting wrap 163 and the guide groove 165 may be simultaneously machined. As described above, if the swirl lap 163 and the guide groove 165 can be simultaneously machined, the guide groove 165 can be precisely machined according to the position and shape of the guide groove 165 designed in consideration of the position and shape of the swirl lap 163.

Further, since the machining of the swirling coil 163 and the machining of the guide groove 165 can be performed simultaneously in one machining operation, the number of steps and the manufacturing cost required for manufacturing can be reduced.

On the other hand, the orbiting scroll 160 may be provided with a back pressure hole 162. The back pressure hole 162 is a passage provided in the orbiting scroll 160 to discharge a part of the refrigerant flowing into the compression chamber to the outside of the compression chamber.

The back pressure hole 162 may be formed as a through hole penetrating the whirl end plate 161 in the thickness direction of the whirl end plate 161. With such a back pressure hole 162, a passage for discharging a part of the refrigerant flowing into the inside of the compression chamber to the outside of the compression chamber through a passage other than the discharge port may be formed on the orbiting scroll 160. In this case, the back pressure hole 162 is preferably arranged on the inner side in the radial direction of the swirl end plate 161, not the back pressure chamber 147 described later.

The refrigerant discharged to the outside of the compression chamber through the back pressure hole 162 becomes a pressure generating source generating a pressure that pulls the gap between the swirling disc 160 and the main frame 140 to closely attach the swirling disc 160 to the fixed scroll 150 side.

That is, when the back pressure hole 162 is formed in the orbiting scroll 160, an intermediate pressure acts between the orbiting scroll 160 and the main frame 140, so that the orbiting scroll 160 can be effectively brought into close contact with the fixed scroll 150 side, and a friction loss that may occur due to friction between the orbiting scroll 160 and the main frame 140 when the orbiting scroll 160 orbits can be reduced.

[ Structure of Main frame ]

Fig. 7 is a perspective view showing the main frame shown in fig. 1 separated.

Referring to fig. 1 and 7, the main frame 140 may include driving

shaft supporting portions

141 and 142, a first supporting portion 143, and a second supporting portion 145.

The driving

shaft supporting part

141, 142 may be divided into a first driving shaft supporting part 141 and a second driving shaft supporting part 142.

The first drive shaft supporting part 141 corresponds to a part directly supporting the drive shaft 130, and the main bearing 101 is provided at such first drive shaft supporting part 141. The second drive shaft support 142 is disposed between the first drive shaft support 141 and the revolving end plate 161, and the drive shaft 130 and the shaft coupling portion 164 coupled to the drive shaft 130 are inserted into the second drive shaft support 142. The first drive shaft supporting part 141 is formed to have an internal space capable of accommodating therein the drive shaft 130 and the main bearing 101 coupled to the drive shaft 130.

The second drive shaft support 142 accommodates the drive shaft 130 and a part of the orbiting scroll 160 coupled to the drive shaft 130. In this case, a part of the orbiting scroll 160 accommodated in the second drive shaft supporting part 142 is exemplified as a shaft coupling part 164 to be described later. The shaft coupling portion 164 may be coupled to the driving shaft 130 such that the orbiting scroll 160 is coupled to the driving shaft 130, and may be received inside the second driving shaft supporting portion 142.

The second drive shaft support 142 is formed to have an inner space not less than a turning range in which the shaft coupling portion 164 turns with the turning of the turning scroll 160. That is, the second drive shaft supporting part 142 is formed to have a larger inner diameter than the first drive shaft supporting part 141, and thus a step is formed between the first drive shaft supporting part 141 and the second drive shaft supporting part 142.

The first support portion 143 is disposed on the side opposite to the orbiting scroll 160. The first support 143 may be formed in a disc shape, and the second drive shaft support 142 may be disposed at the center of the first support 143 in the radial direction. Such a first support portion 143 is disposed opposite to the other side of the whirl end plate 161 so that the whirl plate 160 can be supported.

The second support portion 145 is disposed radially outward of the first support portion 143. The second support portion 145 may be formed in a shape protruding from the first support portion 143 to the outside in the diameter direction of the first support portion 143. Such an outer side end portion in the diameter direction of the second support portion 145 may be formed to be convex toward the fixed scroll 150. The second support portion 145 formed in this manner may be coupled with a frame coupling portion 157 provided to the fixed scroll 150.

A plurality of second support portions 145 may be provided at the main frame 140, and the plurality of second support portions 145 may be disposed at predetermined intervals along a circumferential direction of the first support portion 143.

As an example, the main frame 140 may be provided with the second support portions 145 corresponding to the number of the frame coupling portions 157, and such a plurality of second support portions 145 may be disposed at positions corresponding to the positions of the plurality of frame coupling portions 157.

The coupling between the main frame 140 and the fixed scroll 150 may be performed by the coupling between the frame coupling portion 157 and the second support portion 145 provided in the above-described manner, and since the coupling between the frame coupling portion 157 and the second support portion 145 is performed at a plurality of places, the coupling between the main frame 140 and the fixed scroll 150 may be more stably performed.

The plurality of second supporting portions 145 are preferably disposed outside the orbiting scroll 160 supported by the first supporting portion 143 and outside a region in which the orbiting scroll 160 orbits. When the plurality of second supports 145 are arranged in the above manner, interference between the second supports 145 and the orbiting scroll 160 can be prevented.

On the other hand, a back pressure chamber 147 may be provided at the mainframe 140. The back pressure chamber 147 may be disposed at a side of the main frame 140 opposite to the orbiting scroll 160, more specifically, at a side of the first support portion 143 opposite to the orbiting end plate 161.

In such a back pressure chamber 147, the refrigerant discharged to the outside of the compression chamber through the back pressure hole 162 flows in. As described above, the refrigerant flowing into the back pressure chamber 147 becomes a pressure generating source generating a pressure that pulls the gap between the swirling disc 160 and the main frame 140 to closely adhere the swirling disc 160 to the fixed scroll 150 side. The back pressure chamber 147 may provide an installation space for installing a seal member 190, which will be described later, in the main frame 140.

[ anti-rotation structure of spiral vortex disc ]

Fig. 8 is a view illustrating a coupling structure between the rotation preventing member and the guide groove shown in fig. 1, and fig. 9 is a sectional view illustrating a compression part structure of the scroll compressor shown in fig. 1.

Referring to fig. 8 and 9, a guide groove 165 is formed in either one of the fixed scroll 150 and the orbiting scroll 160, and a rotation preventing member 170 may be provided in the other one of the fixed scroll 150 and the orbiting scroll 160. In the present embodiment, the guide groove 165 is formed in the orbiting scroll 160, and the rotation preventing member 170 is provided in the fixed scroll 150.

Thereby, the guide groove 165 is formed to be recessed in the swivel end plate 161 on the side surface opposite to the fixed end plate 151. Such a guide groove 165 may be formed as a circular groove, and may be formed to be recessed from one side surface of the whirl end plate 161 toward a direction away from the fixed end plate 151.

According to the present embodiment, in the orbiting end plate 161, the orbiting wrap 163 is formed to protrude from one side surface of the orbiting end plate 161 toward one side of the fixed end plate 153. In this case, the orbiting scroll part 163 may be disposed on the center side in the radial direction of the orbiting end plate 161 in the orbiting end plate 161. The guide groove 165 may be disposed outside the swirl coil 163 in the radial direction.

Further, in the fixed end plate 151, the fixed scroll part 153 is formed to protrude from one side surface of the fixed end plate 151 toward one side of the whirl end plate 161. In this case, the fixed scroll portion 153 may be disposed on the fixed end plate 151 at the center side in the diameter direction of the fixed end plate 151.

The rotation preventing member 170 is disposed between the fixed end plate 151 and the swivel end plate 161. Such a rotation preventing member 170 may be provided on the fixed scroll 150, and for this purpose, the fixed scroll 150 may be provided with a provision groove 159. The setting groove 159 may be formed to be recessed in a side surface opposite to the whirl end plate 161 in the side wall portion 155.

The setting groove 159 may be disposed outside the fixed scroll 153 in the radial direction. Thus, the rotation preventing member 170 coupled to the installation groove 159 can be arranged outside the fixed scroll portion 153 in the radial direction.

According to the arrangement structure of the rotation preventing member 170 and the provision groove 159 as described above, the rotation preventing structure configured by the coupling between the rotation preventing member 170 and the provision groove 159 may be arranged outside in the diameter direction of the compression chamber formed by the engagement between the fixed scroll part 153 and the orbiting scroll part 163.

That is, when the fixed scroll 150 and the orbiting scroll 160 are engaged with each other, a compression chamber for compressing a refrigerant may be formed at an inner side in a diameter direction thereof, and a structure for preventing the rotation of the orbiting scroll 160 may be disposed at an outer side in the diameter direction.

Also, the rotation preventing member 170 may be provided in the form of a cylindrical Pin (Pin) having a length extending in the up-down direction. The rotation preventing member 170 may be inserted into the installation groove 159 at least partially, and be tightly fitted into the installation groove 159, thereby being installed in the fixed end plate 151. Also, the rotation preventing member 170 provided in this manner is provided to protrude toward the guide groove 165, and at least a portion of the rotation preventing member 170 provided in this manner may be inserted into an inner region of the guide groove 165.

As described above, the rotation prevention member 170 may be provided in the form of a cylindrical pin having a predetermined diameter, and the guide groove 165 may be formed in a circular shape having a larger diameter than the rotation prevention member 170. The rotation preventing member 170 inserted into the guide groove 165 is revolved around the inner region of the guide groove 165, and the movement of the swirling coil 160 is restricted within a certain range, thereby preventing the rotation of the swirling coil 160.

Further, the rotation preventing member 170 may be formed to have a length deeper than the depth of the setting groove 159 and shorter than the distance between the guide groove 165 and the bottom surface of the setting groove 159 facing each other. That is, the rotation preventing member 170 may be formed to have a length that can be inserted into the inner region of the guide groove 165 even in a state of being closely fitted to the installation groove 159, and may not be in contact with the bottom surface of the guide groove 165 even in a state of being inserted into the installation groove 159 at the deepest.

By providing the rotation prevention member 170 in the above-described manner, it is possible to stably maintain a state in which at least a portion of the rotation prevention member 170 is inserted into the inner region of the guide groove 165, and to prevent friction from occurring between the rotation prevention member 170 and the bottom surface of the guide groove 165 even if the length of the rotation prevention member 170 is increased due to thermal expansion of the rotation prevention member 170.

In addition, the scroll compressor 100 of the present embodiment may further include a ring 180. The Ring 180 is inserted into the guide groove 165, and may be formed in a Ring (Ring) shape having an outer diameter corresponding to an inner diameter of the guide groove 165.

As described above, since the ring 180 is provided to the guide groove 165, the revolvable region of the rotation preventing member 170 is limited in the inner region of the ring 180. When the swirling coil 160 swirls, the rotation preventing member 170 revolves in the revolvable region set by the ring 180, so that the rotation of the swirling coil 160 can be prevented. At this time, the revolution of the rotation preventing member 170 may be performed in a form in which the rotation preventing member 170 contacts the inner circumferential surface of the ring 180 and revolves in the inner region of the ring 180.

According to the present embodiment, the plurality of rotation preventing members 170 are provided between the fixed scroll 150 and the orbiting scroll 160, and the plurality of rotation preventing members 170 are arranged at predetermined intervals along the circumferential direction of the orbiting scroll 160. Also, the guide grooves 165 and the rings 180 provided therein may be provided in the same number as the rotation preventing members 170, and may be arranged at positions corresponding to the positions of the rotation preventing members 170.

By the plurality of anti-rotation members 170, the guide groove 165, and the ring 180 provided in the above-described manner, an anti-rotation effect is achieved at a plurality of points, so that the orbiting scroll 160 can be more stably revolved.

The number of the rotation preventing members 170 may be selected in an appropriate number according to the type and capacity of the compressor. In the present embodiment, the four anti-rotation members 170 are provided between the fixed scroll 150 and the orbiting scroll 160, but not limited thereto.

[ formation Structure and seal Structure of Back pressure Chamber ]

Fig. 10 is an enlarged view showing a portion "x" of fig. 9 in an enlarged manner, and fig. 11 is a cross-sectional view showing a sealing action of the sealing member shown in fig. 10.

Referring to fig. 9 and 10, a back pressure chamber 147 may be provided at the main frame 140. The back pressure chamber 147 may be disposed at a side of the main frame 140 opposite to the orbiting scroll 160, more specifically, at a side surface of the first support portion 143 opposite to the orbiting end plate 161.

The back pressure chamber 147 may be formed to be recessed from a side surface of the first support part 143 opposite to the whirl end plate 161 toward a direction away from the whirl end plate 161. Such a back pressure chamber 147 may be formed in a ring shape around the center in the diameter direction of the first support portion 143. In the present embodiment, it is illustrated that the back pressure chamber 147 is formed in a ring shape surrounding the second drive shaft supporting portion 142, and the pair of back pressure chambers 147 are arranged in a concentric circle shape.

According to the present embodiment, the back pressure hole 162 is formed at the swirling coil 160, and a portion of the refrigerant flowing into the inside of the compression chamber may be discharged to the outside of the compression chamber through the back pressure hole 162 during compression. The refrigerant discharged to the outside of the compression chamber through the back pressure hole 162 may flow into the back pressure chamber 147, and as described above, the refrigerant flowing into the back pressure chamber 147 becomes a pressure generating source generating a pressure that pulls the interval between the swirling disc 160 and the main frame 140 to closely attach the swirling disc 160 to the fixed scroll 150 side.

Accordingly, an intermediate pressure acts between the orbiting scroll 160 and the main frame 140, so that the orbiting scroll 160 can be effectively brought into close contact with the fixed scroll 150, and a friction loss which may occur due to friction between the orbiting scroll 160 and the main frame 140 when the orbiting scroll 160 orbits can be reduced.

In addition, as shown in fig. 2, 9 and 10, the scroll compressor 100 of the present embodiment may further include a sealing member 190 disposed between the orbiting scroll 160 and the main frame 140. The sealing member 190 is provided in the back pressure chamber 147, and may be configured to include a close contact portion 191 and a support portion 193.

The close contact portion 191 may be disposed between the swirl end plate 161 and the back pressure chamber 147 so as to be in close contact with the swirl end plate 161. The support portion 193 is provided so as to be able to be connected to the close contact portion 191 while being inserted at least partially into the back pressure chamber 147.

The support portion 193 is formed as a surface extending in a direction connecting the whirl end plate 161 and the back pressure chamber 147 to each other. The close contact portion 191 forms a surface parallel to the revolving end plate 161, and is connected to the support portion 193 between the revolving end plate 161 and the close contact portion 191.

In the present embodiment, the abutting portion 191 is formed in a ring shape corresponding to the shape of the back pressure chamber 147. Such an abutting portion 191 may be formed in a ring shape having a plane parallel to the whirl end plate 161. The support portion 193 may be formed in a ring shape having a plane parallel to the inner sidewall of the back pressure chamber 147, and may be connected to the close contact portion 191 in a shape of "ᄀ".

In addition, a pair of seal members 190 may be provided corresponding to the case where the pair of back pressure chambers 147 are arranged in concentric circles. At this time, the sealing member 190 provided in the back pressure chamber 147 on the inner side may be provided in a ring shape having a size and a shape corresponding to the back pressure chamber 147, and the sealing member 190 provided in the back pressure chamber 147 on the outer side may be provided in a ring shape having a size and a shape corresponding to the back pressure chamber 147.

The sealing member 190 provided in the above manner can maintain the abutting portion 191 in a state of not abutting against the whirl end plate 161 until the back pressure is formed in the back pressure chamber 147. When the refrigerant flowing into the inside of the compression chamber is compressed, the refrigerant discharged to the outside of the compression chamber through the back pressure hole 162 may flow into the back pressure chamber 147 through a gap formed between the sealing member 190 provided in the back pressure chamber 147 and the back pressure chamber 147.

As described above, the refrigerant flowing into the back pressure chamber 147 serves as a generation source for generating a pressure for closely contacting the swirling disc 160 to the fixed scroll 150 side by separating the swirling disc 160 and the main frame 140, and also serves as a generation source for generating a pressure for closely contacting the sealing member 190 to the swirling disc 160 side.

Thus, the seal member 190, more specifically, the close contact portion 191 is in close contact with the orbiting scroll 160 side while the orbiting scroll 160 is in close contact with the fixed scroll 150 side.

Thereby, a sealed space surrounded by the orbiting end plate 161, the first support portion 143 of the main frame 140, and the seal member 190 can be formed between the orbiting scroll 160 and the main frame 140. That is, sealing between the back pressure chamber and the periphery thereof can be achieved by the sealing member 190 provided in the back pressure chamber 147.

According to the sealing structure formed as described above, the sealing member 190 is provided in a form not fixed to any one of the swirling coil 160 and the main frame 140, and the coupling between the sealing member 190 and the swirling coil 160 can be achieved only by the action of the pressure formed in the back pressure chamber 147.

Therefore, even if the orbiting scroll 160 performs an orbiting motion, friction between the sealing member 190 and the orbiting scroll 160 or friction between the sealing member 190 and the main frame 140 hardly occurs. That is, since the sealing member 190 is disposed such that the sealing member 190 hardly rubs against the orbiting scroll 160 or the main frame 140 during the orbiting of the orbiting scroll 160, the abrasion of the sealing member 190 can be remarkably reduced.

[ action and Effect of scroll compressor ]

Fig. 12 is a perspective view showing a cross ring of a related art compressor, and fig. 13 is a bottom view showing a bottom surface of a swirling disc of the related art compressor.

Referring to fig. 12 and 13, in the scroll compressor of the related art, a spider 10 is generally provided as a rotation preventing member. The cross 10 is disposed between the main frame and the orbiting scroll 20, and may include a ring-shaped main body 11 and a key 13 protruding from the main body 11 toward the orbiting scroll 20.

The orbiting scroll 20 may include a disk-shaped end plate 21 and an orbiting wrap portion formed to be convex in a thickness direction of the end plate 21. In the end plate 21, a key groove 23 is provided on a bottom surface facing the cross 10 and the main frame. That is, the key groove 23 is provided on the surface of the end plate opposite to the surface on which the swirl lap is arranged.

The key groove 23 is formed to be recessed in the bottom surface of the end plate 21, and the coupling between the swirling disc 20 and the cross 10 can be achieved in a manner that the key 13 is inserted into such a key groove 23. The key groove 23 has a length extending in the diameter direction of the end plate 21 so that the key 13 of the cross ring 10 can move inside the key groove 23.

Further, a back pressure hole may be formed in the orbiting scroll 20 so as to penetrate through the end plate 21 of the orbiting scroll 20. A portion of the refrigerant flowing into the compression chamber may be discharged to the outside of the compression chamber through the back pressure hole. As described above, the refrigerant discharged to the outside of the compression chamber through the back pressure hole flows into the back pressure chamber 25 to form a back pressure so that the orbiting scroll 20 is in close contact with the fixed scroll.

Unlike the scroll compressor of the present embodiment in which the back pressure chamber 147 (see fig. 9) is formed in the main frame 140 (see fig. 9), the back pressure chamber 25 is formed in the orbiting scroll 20 in the scroll compressor of the related art.

A back pressure chamber 25 of the related art scroll compressor is formed in a bottom surface of the end plate 21 opposite to the main frame. This is because the back pressure chamber 25 must be formed between the main frame and the orbiting scroll 20 in order to form a back pressure for bringing the orbiting scroll 20 into close contact with the fixed scroll.

However, in this case, there is a problem in that the key groove 23 and the back pressure chamber 25 are formed on the same surface on the end plate 21. In order to smoothly form the back pressure, the key groove 23 and the back pressure chamber 25 should not overlap, and therefore, in consideration of this, the key groove 23 should be disposed at a position further outside than the back pressure chamber 25.

However, if the key groove 23 and the back pressure chamber 25 are arranged in the above manner, accordingly, the entire size of the swirling disc 20 must be increased. That is, only the size of the orbiting scroll 20 is increased without particularly improving the performance of the scroll compressor, so that there is a problem in that only the size of the scroll compressor is increased.

In contrast, as shown in fig. 9, the scroll compressor 100 of the present embodiment is designed such that the configuration related to the formation of back pressure and the configuration related to the prevention of the rotation of the orbiting scroll 160 are not arranged on the same surface of the orbiting scroll 160.

That is, the back pressure chamber 147, which is one of the components related to the formation of the back pressure, is formed in the main frame 140, not in the orbiting scroll 160. The guide groove 165, which is a structure related to rotation prevention, is formed in the orbiting scroll 160, and is formed on a surface of the orbiting scroll 160 opposite to the surface facing the main frame 140.

The guide groove 165 is formed at an opposite surface to a surface opposite to the main frame 140, and may be implemented by disposing the rotation preventing member 170 between the orbiting scroll 160 and the fixed scroll 150 instead of between the orbiting scroll 160 and the main frame 140. Also, the rotation preventing member 170 is provided between the orbiting scroll 160 and the fixed scroll 150 instead of between the orbiting scroll 160 and the main frame 140, and it may be implemented by providing the rotation preventing member 170 in the form of a Pin & Ring (Pin & Ring) instead of a cross Ring.

According to the arrangement structure of the back pressure chamber 147 and the guide groove 165 as described above, the back pressure chamber 147 and the guide groove 165 can be respectively provided at positions that do not affect each other at all. Therefore, even if the back pressure chamber 147 and the guide groove 165 are disposed at positions overlapping in the extending direction of the drive shaft 130, that is, in the vertical direction, the presence of the guide groove 165 does not adversely affect the formation of back pressure, or the presence of the back pressure chamber 147 does not adversely affect the operation of the rotation preventing member 170 for preventing rotation.

Thus, it is not necessary to unnecessarily increase the size of the swirling coil 160 in order to form the back pressure chamber 147 and the guide groove 165, so that the scroll compressor 100 having a compact size and excellent performance can be provided.

On the other hand, since the back pressure chamber 147 is disposed between the orbiting scroll 160 and the main frame 140, an intermediate pressure acts between the orbiting scroll 160 and the main frame 140. In general, the scroll compressor 100 having such a structure is classified into a lower back pressure scroll compressor, and conversely, a scroll compressor having a structure in which a back pressure chamber is disposed at an upper portion of a fixed scroll and a orbiting scroll is classified into an upper back pressure scroll compressor.

The upper back pressure scroll compressor has a back pressure chamber of a fixed form, and thus has advantages in that the fixed scroll is less likely to tilt and the sealing of the back pressure chamber is also good, but has disadvantages in that a structure for forming the back pressure chamber is relatively complicated compared to the lower back pressure scroll compressor.

In contrast, the lower back pressure scroll compressor has an advantage in that a structure for forming the back pressure chamber is simple. However, in such a lower back pressure scroll compressor, there is a problem in that, since the back pressure chamber is located at the bottom surface of the swirling scroll which performs a swirling motion, the shape and position of the back pressure chamber are changed according to the swirling motion, and therefore, the possibility of generating a tilt in the swirling scroll and generating vibration and noise is high, and the abrasion of the O-ring inserted for preventing the leakage of the back pressure chamber is fast.

In view of this, the scroll compressor 100 of the present embodiment proposes the following constitution: the back pressure chamber 147 is formed on the main frame 140 instead of the orbiting scroll 160, and the sealing member 190 is provided not to be fixed to any one of the orbiting scroll 160 and the main frame 140. The scroll compressor 100 of the present embodiment having such a configuration can provide the following effects.

First, the back pressure chamber 147 is formed on the main frame 140 instead of the orbiting scroll 160, and thus it is possible to reduce the possibility of the orbiting scroll 160 tilting and the generation of vibration and noise caused thereby, as compared to the case where the back pressure chamber is formed on the orbiting scroll 160. This is a result of a design in which the back pressure chamber is formed on the main frame 140 instead of the swirling disc 160 so that the shape and position of the back pressure chamber are not changed according to the swirling motion of the swirling disc 160.

Second, the sealing member 190 is provided in a form that is not fixed to any one of the orbiting scroll 160 and the main frame 140, and performs a sealing function using back pressure formed at the back pressure chamber 147, so that abrasion of the sealing member 190 can be remarkably reduced.

Third, according to the scroll compressor 100 of the present embodiment, as described above, since the lower back pressure scroll compressor in which the back pressure chamber 147 is formed between the orbiting scroll 160 and the main frame 140 is provided, a complicated structure for forming the back pressure chamber may be omitted.

That is, the scroll compressor 100 of the present embodiment can be provided in a form of omitting a plurality of complicated structures provided for forming the back pressure chamber in the related art upper back pressure scroll compressor, and thus can provide an effect of reducing the manufacturing difficulty and the manufacturing cost.

The present invention has been described with reference to the embodiments shown in the drawings, but this is merely exemplary, and it should be understood that various modifications and equivalent other embodiments may be made by those skilled in the art. Therefore, the true technical scope of the present invention should be defined by the appended claims.

Claims

1. A scroll compressor, comprising:

a case having a closed inner space;

a fixed scroll disposed in an inner space of the casing;

a swirling disc combined with the fixed scroll to form a compression chamber and performing a swirling motion; and

a main frame supporting the swirling coil,

the orbiting scroll includes:

a swirl coil engaged with the fixed scroll to form the compression chamber; and

a swirl end plate disposed between the swirl coil and the main frame,

a guide groove is formed in either one of the fixed scroll and the swirling scroll,

an anti-rotation member is provided on the other of the fixed scroll and the orbiting scroll, and the anti-rotation member is inserted into the guide groove so as to be capable of revolving inside the guide groove.

2. The scroll compressor of claim 1,

the guide groove is formed to be recessed in a side surface of the swirl end plate opposite to the fixed scroll,

the rotation preventing member is provided to the fixed scroll and is provided to protrude toward the guide groove.

3. The scroll compressor of claim 2,

a plurality of the guide grooves are arranged at predetermined intervals along a circumferential direction of the whirl end plate,

the plurality of rotation preventing members are arranged in the same direction as the plurality of guide grooves and at intervals.

4. The scroll compressor of claim 2,

in the fixed scroll, a concave setting groove is formed,

the rotation preventing member is tightly fitted to the installation groove so that at least a part of the rotation preventing member protrudes toward the guide groove.

5. The scroll compressor of claim 4,

the rotation preventing member is formed to have a length longer than a depth of the installation groove and shorter than a distance between the guide groove and a bottom surface of the installation groove facing each other.

6. The scroll compressor of claim 1,

a back pressure chamber communicating with the compression chamber is formed in the main frame on a side opposite to the orbiting scroll.

7. The scroll compressor of claim 6,

the main frame includes:

a first support portion configured to be opposed to the other side surface of the whirl end plate to support the whirl coil; and

a second support portion arranged outside the first support portion in a diameter direction to be coupled to the fixed scroll,

the back pressure chamber is formed to be recessed at the first support portion.

8. The scroll compressor of claim 7,

the back pressure chamber is formed to be recessed from a side surface of the first support portion opposite to the whirl end plate toward a direction away from the whirl end plate, and is formed in a ring shape surrounding a center of the first support portion in a diameter direction.

9. The scroll compressor of claim 8,

a pair of the back pressure chambers are arranged in the shape of concentric circles.

10. The scroll compressor of claim 6,

further comprising a sealing member disposed between the swirling coil and the main frame and disposed in the back pressure chamber,

the sealing member includes:

a close-fitting section disposed between the rotating end plate and the back pressure chamber so as to be able to closely fit to the rotating end plate; and

and the supporting part is at least partially inserted into the back pressure cavity and connected with the clinging part.